Power generating and transmitting machinery.



- H. D. WILLIAMS. POWER GENERATING AND TRANSMITTING MACHINERY.

APPLICATION FILED SEPT-21,1911.

Patentad Sept. 12, 1916.

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POWER GENERAHNG AND TRANSMITTING MACHINERY.

Patented Sept. 12, 1916.

4 sHEETs-sHEETI3- APPLICATION FILED SEPT. 2l, 191 I.

manif/MWI- H. D. WILLIAMS.

POWER GENERATING AND TRANSMITTING MACHINERY.

APPLICATION FILED SEPT. 21, 19H.

Patented Sept. 12, 1916.

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HARVEY D. WILLIAMS, 0F NEW YORK, N. Y., ASSIGNOFI T0 TILIE WATERBURY TOOL COMPANY, OF WATERBUJRY, CONNECTICUT.

POWER GENERATING AND TRANSMITTING MACHINERY.

Specification of Letters Patent.

Patented Sept.. 12, 19115.

Application filed September 21, 1911. Serial No. 650,554.

To all whom t may concern Be it known that I, HARVEY D. WILLIAMS, a citizen of the United States, and resident of the borough of Manhattan, city, count-y, and State of New York, have invented certain Improvements in Power 'Generating and Transmitting Machinery, of which the following is a specification.

My invention relates to power plants of the type commonly used for propelling automobiles and motor boats wherein the power developed by an internal combustion engine is transmitted through a speed changing and reversing mechanismto a propeller shaft or its equivalent. For the transmission I use a variable speed gear of the type in which a liquid (preferably lubricating oil) circulates through a pump and a motor, the volumetric rigidity of the liquid imparting a-quality of positiveness to the transmission, and in which an infinite series of speeds is obtained by varying the stroke of the pump. In my which 1 is the pumping engine, 2 is the mois a section of the pumping engine at right angles to the crank shaft in theplane of a cylinder axis and looking as indicated at A Fig. 1. Fig. 3 is a parallel section in a plane midway between two cylinder axes as indicated at B Fig. 1. Fig. 4 is a section through 'three adjacent cylinder aXes looking as indicated at C Fig. 2. Fig. 5 is a partial plan view of the pumping engine showing four tion parallel to Fig. 4 in the plane of the aXes of the pump cylinders as indicated at E Fig. 2 but with certain moving parts in different positions. Fig. 7 is a detail plan view, partly in section, showing chiefly the pump plunger and parts connected therewith; Figs. 8, 9, 10, and 11 are vertical sections of a combined safety and reversing valve and its casing, showing the valve in four different pqsitions, Fig. 9 also illustrating the mechanism for shifting said .v-alve; Fig. 12 is a central vertical section through the pump, looking as indicated at F in Fig. 1; Fig. 13 is a vertical section 'of a modification, said view being taken on a plane corresponding to Fig.'2; Fig. 14 illustrates said modification by a sectional View corresponding to Fig. 12; Figs. 15 and 16 are vertical sections of the safety valve and its casing employed in this modification, showing the said valve in two dierent positions; Fig. 17 is an elevation of an arrangement embodying my invention, which dispenses with a separate reversingI valve, and in which thel driving shaft and the driven shaft are alined and may be coupled for a direct drive; Fig. 18 is an elevation of another form of my invention in which the engine and motor shaft are geared together.

Referring to Figs. 2, 3, and 4, the engine cylinder 8, driving member or piston 9, piston pin 10, and connecting rod 11, differ in no essential respect from the parts commonly used in engines of this type. The same is true of the engine valve gear and other parts which are for that reason omitted from the drawings and only those partsshown which relate to the present invention. Thus the crank shaft 12 has five cranks (or some other odd number) equally spaced around the circumference of the crank circle whereas common practice favors the 180 spacing ofan even number.

The reason for this difference is that in my i invention the determining factor is theimportance that the pump delivery shall be as free as possible from pulsations and it being well known thatf'that quality is characteristic of the first arrangement of cranks noted above. With `five cranks (supposed numbered in their order along the shaft) the best order of sequence in the revolution islst, 3rd, 5th, 2nd, 4th. This gives a favor-4 able balance of the inertia forces of all moving parts including the new group which I "fio Y components of forces acting on the lever 15.

'On each sideof lever 15 there is a rectangu.

lar channel in which slides a block 20. Blocks 2O turn on the vpins 2l whichare l25. sliding, connection with the stationary part 18'. The constraints of the-`sliding conne'c# tion betweenthe last named parts consist of have added in the process of converting there simple engine into a pumping engine. The

aggregate group'associated with each crank is the same. for all, so that a'description of lone will suilice. The connection 'between thefnew pump group and the old engine groupoccurs at the piston pin 10. Engaging with this pinon either side of the engine connecting rod is a pump connecting 'rod 13 the forked lower ends of which enl gage by the pinsl/l with the lever the shape of which is better understood by reference to Fig- 7. Fixed to thelever 15 is the pin 16 which engages with the pump plunger17. Pump plunger 17 is constrained to .move in a vertical line by the boreof pump cylinder 18 Fig. 6 assisted' by thetwo upward prolongations 1 9 of the cylinder Walls, said prolongations being so disposed as to most eiiectually resist the horizontal carried by the brackets 22 `-which have a A thelat contact between brackets 22 and the v the plate l23 "side of 8.

'. Referring to F ig; 5 it 4under side of 8, a'tongue on 22 engaging witha slot, in Sand the flat contact between (secured to I22) I andthe upper plate 23 is secured' to thejse'veral brackets 22 bythe screws 2 4.' The use of a single plateV l23 insures` the exactl alinement at all times of theseveral"pins 21l and facilitates thel simultaneous 'and' parallelfmovement of the l` 4b said pins in afhorizfontal direction. To in? sure the parallelism of .this movement I` "a 'parallel motion" consisting of 'two equal l bell cranks 25', two equal connecting' rods 26,

'fandone long connecting 'rod 27 ;1 said parts being pivoted'together in the order shownv and the distance between the pair o f pivots lcarried bycthe parts 8,523 and '27 being. f v equal. An armv of one bell crank is slightly y vprolonged and carries a manual control handle28. Thus at willmay the 'pins' 21 be .j -lmovedto-an'dfro horizontally from the position shown in Fig. 3 4through the posi'- tion shown in-Fig. 2 to anextreme position I' (not shown) determined -inthiscaseby the `vcontact-of bracket`22 with the `casing Vat 88. In F1g..3 andFig. 6 the pins 21 are in alinement with the pins 16, the pump plungers .A jarehel'd immovable and the turning over of 1 the engine yresults merely in arocking movement 'oflever 1 15 about the fixed center of away from the position shown inFig. 3 the pump 4stroke is. gradually increased from 'zeroto a maximum thestroke being` in fact i eaproportienalto the displacement of the pin 'is Seen that a single "@21. B'y aid of the iinkwork heredisclosed it evidently possible from a moderate small in diameter Vand the angular movements are small compared to that of the crank shaft. `At the piston pin the movement is especially small and the correspondingly slightangularity ofthe pump connecting rodsignifies very little side pressure and consequent friction between engine piston and cylinder. Also as influencing side pressure the method employed for reciprocating the' pump plunger is especially favorable. Thus the mean value of the side pressure between the pump plunger and the cylinder wall due to the angularity ofthe lever 15 is about one half what'it would be if the plunger were drivenffroma crank through a connecting rod having a maximum 'angularityequal to that of the lever 15.' Beysides'which the pump plunger, by virtue of its pumping oil, is ideally lubricated. The

'transmission of power being equally divided among the several pump linkworks it follows that no part of any linkwork need be strongerthan necessary to do the work of -o'ne pump. On the other hand we have in the engine linkwork (before the pumps were added) two turning joints (crank pm and main bearing)v each with an angular movementv of af'complete revolutionarid large enough in diameter to transmit' the combined power of the several engine c'ylin-4 'ders, together with a connectingrod-Qf large angularity and proportionate side ressure between piston and cylinder wall w ere the,y i l of the several pump strokes. Especially vis this the case if we suppose the engine to be of the vtwo cycle type since here7 with each downward stroke a working stroke, and

with each associatedI pump taking just the amount of energy developed .in the engine, it is evident that comparatively little stress will be thrown on the crank shaft, a circumstance which permits of lighter construction and consequent further increase of efficiency.

The pump draws its supply of oil from` the duct 29 by Way of the check valve 30 and discharges through the check valve 31 conditions for. lubrication'are not'the best.

AAfter the pumps areadded according` to my invention the principal function of the crank shaft is to preserve the `time sequence into the duct 32. For purposes of illustration check valves 3() and 31 are represented as being guided on a small tension rod 75 and held against their seats by light helical springs. ln actual construction I use a type of check valve better adapted for high speeds but not Veasily shown in one view.

y The ducts 29 and 32, extending the whole length of the engine frame, are closed at the ends and communicate by the flanged connections 33 and 34 respectively with the interior of the safety and reversing valve 6. Fromthe disposition of the check valves v30 and 31'it is -evident -that the highest occurring pressure will always be in duct'32 and connection 34.

The combined'safety and reversing valve comprises a valve body v35 Fig. 8 having four interior annularports, two of which communicate upward with the flanged connections 33 and 3ft already noted and the alternate two communicate downward with the similar `connectionst and 5 and through them with the like numberedl circulating pipes shown in Fig. 1. The valve proper 36 is a balanced piston valve with a central l longitudinal opening and an outside circumnormal lpositions-one for going ahead and terential channel ot width sui'iicient to span two adjacent ports inthe valve body. The valve 36 is moved by the valve stem 37' which passesv out through the stuliing box 38. Mounted on the outer end of the valve stem is the spring'box 39, the spring 40 and the plug 41 the latter screwthreaded into the end of the .spring box and having a squared endfor turning to adjust the tension on the spring. The other end of thev spring bears against' collar t2 on the. valve 'stem which in turn bears. against the spring box so that the torce 4of the spring acts to l hold the valve stem and the spring box in the relative positionfshown in Fig. 8.

Regarded as a reversing valve the two one for backing-are shown in Fig. 8 and v'Fig'. 10 respectively. ln-Fig. 8 port 3ft is the two collars ttl in communication with port 5 and port'33 with port 4. In Fig. 10 these relations, are

reversed,l 34 being in communication with t and 33 with. For shifting the' valve for A reversing and for holding'it in either'ofthe normal positions -lt provide the manual le 43 Fig.- 9 lwhich ispivoted to ycontrol han the stationary frame at 4A and carrles at its lower end theA pin 45 which engages. between `ati-on the outside of spring box 39.

rlihe 'functioning of the valve as a safety valve for the ',reliet` ofiexcessive pressure when going ahead is shown in Fig. 9. As.,

, already noted the highest occurring pressure is always in the connection 34 which is in tree communication through the center oit the valve with that end of thecasing vwhere the valve stem 37 passes out through excessive pressure by providing a by-pass since in Fig. 9 all four ports arey 1n free communication with eachother as a result of the valve lands having been made narrower than the'valve ports'. ln like manner an excessive pressure while backing is automatically relieved by the movement of the valve from the Fig. l0 position to the Fig. 1l position. e

By means of a plurality of pumps oi' the kind disclosed acting in concert under the timing control ofA a single crank shaft it is evidently possible, under conditions of constant revolutions of the crank shaft, toproduce a fairly steady flow through the fluid passages '4 and 5 and the motor 2, the velocity of flowv and therevolutions of the motor-being variable at will between zero and a maximum; and by aid of the reversing valve the said flow and revolutions can 'be immediately reversed from any value,

plus orminus,.to the corresponding .value of the opposite sign. in order however, to prevent the possible stalling of the engine by the inertia of a too sudden reversal (as for example when the motor is geared to a drawbridge) l provide ameans which may befused for interlocking the two lmanual control handles 28 and 43 (for changing the speed and for reversing respectively) so that reversal can be attemptedv only when the speed is zero. 'One of the brackets 22 loa (the one lying in theplane of thecentral positio-nsoit'the control handle 43) has a projection 47 long enough tb obstruct the movement of handle 4:3 Fig. 9 except when bracketf22 is in the zero position Fig. '3

as regards stroke of pump and yspeed of motor.-v With this arrangement it 'is evidently impossible to' shift the reversing leverwithout having first moved the speed contr'olfhandle to the zero position. .Variable'speed gears of'this-ty e 'require some insurance against loss (by eakage) of the integrity of the fluid connection. In the present case this4 insurance consists of means for collecting leakage' vand an auxiliary pump adapted' to return to the fluid connection such leakage. Thus oil leaking-from the `fluid connections through the working joints at thefrnotor end of the speed gez'tr 1s conveyed by the pipe t8 Fig. 1 to thev .pocket t9 Figi 3 lwhich catches also'any leakage from the working joints ot the pump.- The'only leakage from high pres'- aaa sure working joints-not thus accounted for Lis the very small. amount from the valve stem stuffing box 38. Hence, 'so far as the mere replenishment of leakage is concerned` working joints but often also at permanent joints as Well. Even if the sucking of air is prevented by immersion in oil still the maximum speed at wh-ich the machine can be run is apt Ito be 4determined by the production at points of lowest-pressure in the circulatory passages of voids or partial.

vacuums theresult of a too close approach to zero absolute pressure. For maintaining a pressure higher than atmospheric in the vlow pressure ductand for returning to said duct and against said pressure the oil .that

f hasleaked past the working joints of the speed gear I use the combined replenishing` and back pressure pump, 7. The eccentric 50 Fig. 12 is keyed to the engine crank shaft i 12 and the drain pipe 51 is in communica- 1 tion with the pocket 49. The stationary part or frame of the pump is built in the form of a boX 52 to serve as a storage reservoir and so thatallworking joints of the pump may be immersed and so. that joints of whatever kind which are subjected to less than atmospheric pressure cannot in any case leak airbutonly oil. The plungerk 53, thcconnection from the plunger togthe` eccentric' 50, the suction and dischargecheck valves 54 and 55 arel without novelty in cnstruction or operation. In a cylindrical r'el cess however in the lower part of box 52 there is .a sliding piston '56' arranged to vacillate between the'force of spring 57 on vone side and the discharge pressure of the pump on the other. Under anexcess ofthe latter the piston 56' moves to the right against -the spring andl shuts off at 58 the I access of oil to the suction *valve 54. Otherwise there is free access from the tank space to the suction valve through the hole 59 `andthe holes inthe-spring adjusting nut 60. Thenut 60 is rotated to adjust the spring tension by means of the square rod 61 whichengagesrby ground joint with the plug 62 and isaccessible on the outside of lthe tank. l The final discharge of the pump -A 'is through the opening 63 right-into the" flow pressure duct 29. In order to operate as intended the capacity of the'pump working continuously at full stroke mustn-be '1 enough tomore thanv take care of the maxi,- mum-amount vof leakage from'all parts of the variable speed gear. Such being the case it is evident that, with the constructionl shown, the ,pump working continuously canj sucking of air be vprevented not only at the not fail toj maintain in the low pressure duct the pressure for which the spring 57 is set.A Nor can the pump exceed that pressure much less create an excessive pressure owing to themanner in which the pump is governed by throttling its suction. Voids will of course be created in the suction passages ,during each suction stroke of the pump but these voids will close up and disappear during the nextcompression stroke since there is no opportunity for access to the voids of anything but oil and its vapor.

Figs. 13, 14, 15 and. 16 show certain changes which follow more or less imperatively from an important though inconspicuous alternative construction of the linkwork in Fig. 13. The alternative consists in permitting'pin 21 to assume a position between pinsl 14 and 16. In other words the movementof bracket 22 to the left carries pin 21 beyond pin 16 instead of only to pin 16 as heretofore. The advantage of this construction is that it permits of the elimination of the reversing valve by arranging all speeds, forward and reverse, in a single series cordinate with a corresponding series of positions of a single control lever. In order to derive this advantage however, it is necessary to replace the check (fluid operated) valves of Fig. 2 with a positively operated valve such as 64 Fig. 13. Here we have a balanced piston valve with a middle land wide enough to cover' the cylinder port 65 and having a .central longitudinal opening to prevent the blind pocket at the right hand end ofthe valve from interfering with its. freedom of movement. The valve is reciprocated by a connecting rod and an eccentric whose shaft, through chain gearing 66, is driven from ,the engine crank shaft at the lsame speed as the latter and in the same direction. From generalprinciples of valve setting we know that the valvel must be at mid stroke (in thel act of closing one port and opening another) when the pump plunger is at the end of its stroke, a condition which is realized in this particular case by setting the eccentric radius parallel to the engine crank radius.

In operation suppose the crank to be on the lower dead center and turning in the direction indicated by arrow 67. The engine piston is about to begin 4an upward stroke,

hence the pump plunger is about to begin a downward or pressure stroke and has just nished an' upward or suction stroke. Valve i 64 is moving to the right. It has just closed a passage between 65 and duct 69 which, having :been in communication with the pump cylinder during a suction stroke, is therefore the low pressure duct. Also valve 64 is about to open a passage from 65 to 68 which is therefore the high pressure duct.

If pin 21 is supposed moved to the right to some position such that pin 16 lies becasion requires.

mechas Y tween pins 14 and 21 then, reasoning `as in the last paragraph, pump plunger 17 will have just finished a pressure stroke. Valve 64 has just closed a passage from 65 to 69.

Hence 69 is the high pressure duct, and 68,

with which "communication is about to loc'y opened, istherefore the low pressure duct.

The functions of ducts 68 and 69-have been reversed by the supposed movement of pin being parallel to the radius of the associated crank. The possibility of driving theeccen tric shaft in the reverse ldirection bythe use of spur gearing instead of chain gearing as also the elimination of the eccentric shaft altogether and placing the eccentrics on the 'crank shaft will occur 'to anyone familiar with this class of machinery.

`Since at any time either of the -two iducts 68 and .6 9'may have to act` as thev low pressure` duct, it becomes necessary to connect the replenishing and back pressure pump to both ducts and to so arrange the connection that the discharge from the pump will autoinatically shift from one to the 'other as oc- Fig. 1'4 shows the pump with two dischargeorifices 70 and 71 and Fig. 13 shows the manner of connecting these orifices with ducts 68 and.69 'through l the circulating pipes 4 and 5 respectively.' As parallel branches" of a single discharge,

' the two passages 7 0 and 71 Fig. 14 are fitted with check valves 72 the direction of the valves are arranged in axial alinement with each .other and so that which ever valveis heldl shut by high pressure in its associated duct that valve will, `by contact with the other valve, hold the other valve open. Thus there will be the same freedom of communi cation betweenthe governing piston 56 and the low presure duct thatthere is inFig 12 -where the low pressure duct is always the same. v e

' For relieving'excessive pressure in the fluid connections la safety valve is required which, like the replenishing pump,` will function automatically when there is a reversal i'n the functions of pressure ducts. Fig. 15 shows avalve which fulfils this requirement and which servesl also `as a 'manually controllableley-pass.

The valve is placed as a cross connection bei manillev Circulating Pirese and 5, rs

- valves open.

` between ports discharge flow. The

-pletely the high-and low inserted in the latter communicating with the flanged connections on the valve body 74 and 76 and through these with two interior annular ports 77 and 78. Piston valve 79 is balanced with respect to pressures in both ports. It also closesboth portsy at all times with respect to the region80 comprising the interior of the piston`valve and the two ends s of the valve body. ln its normal or closed condition Fig. 15, valve 7 9 shuts 0E ports 7 7. and 78 with respect toteachother. From ,1

each of the connections74 `and 76 a small passage leads past a'ballscheck .valve into 'i the region 80 toward which the ball check- 'If therejis a difference/of pressure between the connections 74 and 7 6` the greater pressure will prevail-throughout the region 80 since said greater pressure will hola Shut the eau Checkivaive in uw passage leading to the other or low pressure.

the region 80 will, with respect te the valve stem 81, result in an unbalanced4 force tending to .push the valve stem' outward and..

move the vvalve toward the open position high pressure the valve stem 1s equipped with a spring and spring box (similar to the parts already described in connection with the cornbined safety and reversing valve) by which shut and by means of which, asV a manually con'- trollable bypass, the valve is openedv orv the valve, as a safety valve, is held closed as desired.

Fig. 16 showsthe opened gard to pressures,

,valve as having been of disconnecting the' motor fromthe pump-- ing engine when the latter is standingidle. As va safety valve Fig. 16A would show the handle and spring box inthe dotted position the movement ofthe valve having comv Mill f pressed the spring an'famount equal to the movement. l Fig. 17A shows one type of general arr'an'ge` H ment of my invention4 whichdispenses with A;

the separate reversing. valve. rangement 82 is the 'reversing pumping efi gine Fig. 13 pass valveF'ig. l'placed 'as a crosscounectio'n' between the circulating pipes4 .and

5. The motor 2 is of a size or capacity such that, within its range'ofspee'ds'there isincluded thespeed'of theengine' crank by hand for a'by-pass without re-` and perhaps as a means l are.' and 83- 1s the'safety andbyiat shaft. The propellershaft 'extendsv com-l through the motor and presents "a free' end in close proximity: to theend of the engine crank shaft and in axial alinement therewith.- 'A clutch 84 of any type, but shownl as a simple-'jaw clutch, is provided forI coupling propeller shafts.

rangementfis to provide an eXtra resource 1n together-the engine and rIl he object of this -aret connection. The greater pressure acting in Y- mm Fig. 16 which movement will relieve: the

byl opening a communication 77 and 78; The outer end of .v

case of breakdown and also to provide a direct and probably more ve'licient drive in cases where there is a predominating speed *suchl as full speed ahead?. Inv operation the revolutions of -the motor are brought to.' somewhere near the revolutions of the en`.

gine by means of the variablespeed gear.

opento, take care ofthe circulaticn through '-xfthe motor, after which the stroke -of the "pump'isreduced to zero thus stopping all pa'ss."In-order to" reduce as lmuch as pos- Thevclutch is then connected and the safety 'E-valye takes care of anylackfofsynchronism v ubetween the"V direct drive ll'dthevariable speed. drive. l:The by-passgisthen set wide circulation between the pump and the by,-

sible the resistance to-the motor circulation the b'y-pa'ss into the motor the engine crankishaft I have to. sacrifice vcertain advantages which the engine derived froml combining. it withl the pump. There are 'cases -however where an apparently',y triling'd-iiference of `'eiiiciencyin .favor of the direct drive will justify making' pro- '4 vision for it.: i

- fering 'from Fig.l 17 primarilyin the fact that the motor is of so much greate1 ca# pacitythat its range of speed does not in'- 1 clude the speed` ofthe engine, the maximum revolutions of the motor being in fact 'only a' fraction. of the revolutions of the f" engine. In thiscase the engine and motor -vshafts aregeared together ina velocity ra- 4Q tion and provision isj-made for sliding the gears out ofengagement orfor disconnect tio 'approximately equal to the, said fracl `ing. onejof Athe gears' and allowing it to turn idly on its shaft. InvFig. 1 8 the gear 85is 86 turns freelyon the engine shaft when not keyed to they propeller, shaft andthe pinion coupled "theretov the friction clutchV 87.

' ments, 'such The direct'drive feature of Fig. '17 and the geareddrive'feature iof Fig. 1 8fare evi-` dently just as applicable to generalarrangeas Fig-1, wherethe pumping l. A powerv vtransmission' v comprising a pump, ai motor adapted to bevoperatedby fluid under pressure, connections from said motor to the inlet and to the outlet of the pump, a safety valve arranged tobe moved "in one direction byany .excessive pressure y suchfmovelnent to establish a direct commu-* nieation between them, a spring one end occurring in one of'said connections, and by of which is operatively connected with said valve and tends to move it in the opposite fopen the throttle valve against said vpresdirection, and a lvalve-shifting member engaging the other end of said spring.

2. A power transmission vcomprising a. pump, aunotor adapted to be operated by fluid under'pressure, connections from said motor`-to-theinletand to the loutlet of the pump, a reversing valve for governing the direction in which vthe fluid travels'through the motor, a by-pass between-said connections, rand means, operating on said valve,

a replenishing pump having a piston arranged to work in said cylinder, `one end of said piston being exposed to the interior of said receptacle, a suction connection from said receptacle to the replenisliing pump at 9 0 the lother end of said piston, a throttle valve controlling said suction" connection, adelivery connection from vthe replenishing f v vpump to thatconnection through which thev Fig. 18 showsa'general arrangement dif-[ having a surface'exposed to the pressure of the fluid contained insaid delivery connection, 1n ysuch a manner that such pressure will vtend to close the "valve,vand means acting in opposition to said pressure to keep the throttle valve open:

A .power transmission comprising la pump, a motor adapted to be operated by fluid under pressure, connections from said motor to the inlet and to the youtlet of the pump, a receptacle adapted to contain a supplyof fluid v-a'ndfhaving a cylinder open- .ingfintothe receptacle, a replenishing pump having a pistonarranged to work in said cylinder, a 'suction connection from said receptacle-to the replenishing pump 'atthat Iendiof the piston which faces away from lsaidl receptacle, a throttle valve'controlling said suction connection, a delivery' connec- 115 tion v`from the replenishing pump to thatv connection through which the operating fluid returnsfrom the motor tothe firstnamed pump, said throttle valve having a surface exposed to the pressure of the fluid contained in said vdelivery connection, in such a' manner that such pressure will tend to-close'the valve, and a spring tending to sure.

A5. A lpower transmission comprising a pump, a motor adapted to be operated by fluid under pressure, connections from said.

' of-said pump.

I ec.

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. motor to the" inlet and to the outlet of theif: pump', a receptacle adapted tov-contain asup-y ply of fluid and having a cylinder opening the vtiret-namedpump, and means for gov- 6. A power transmission 'comprising a pump, a motor adapted to beoperated by` f fluid under pressure, connectionsyfrom said-i motor to. the inlet and to the outlet ofA the; pump, a receptacle adapted to contain a supi' v ply of Huid and .having a-.cylinderopentov' said receptacle, a replenishing pump having a piston arranged to work in said cylinder j and to take fluid from said receptacle and to deliver such Huid `milder-' pressure to that connection through which the operating fluid returns fromthe motor tov they Iirst- (named pump, and'means for throttling. the l flow of Huid propelledbysaid replenishingpump inaccordance with the delivery side of said pump.,

pressure on the 7. A powerf transmissioncomprising` a pnmp, a motor adapted't'o bef-operated lby `fluid under pressure, connectionsfromisaid motor to the inlet 4and to the-ou'tlet-of` the Y' pump, a receptacle adapted to contain a supply ofiiiid, means forcollecting leakage of pelled by said pumps.`

the operating fluid .and deliveringit to said receptacle, a replenishing pump open to 'the' lower portion of the receptacle and arranged lto to 'take iuid from -said receptacle and to Vdeliver it under, pressure to that vconnection through' which `the o erating fluidreturnsl from thel motor to th and meaiis for governing the action of the,

en first-named pump,

replenishing pumpaccording to thepressure on the delivery side of said pump.

8. vAr power 'transmission comprising'al pump,' a motor adapted -to`be operated by-v fiuid under pressure, connections from said.

motor to the inlet and tothe outlet yof the' pump, means for collecting leakage of-'the operating fluid, a replenishing pump' having a piston oneend of 'which is permanently exposed .to the collected leakage,` while. fthe other end .of the piston is arranged to take such collected leakage and 'to 'deliyer it" un- Ader pressure to that 'connection through which the operating .fluid returns. from the .y ..4 motorto the firstmame'd pump, and means'- ifor governing the action of the` replenish-1 ying pump according to the pressure on 'they delivery side 'of said pump,

v'A power transmission comprising an internal combustion engine having a plural-` ity-fbfhvdriving members, a. shaft having a 14.' :A-:power transmission .co1nprlisin` Ia corresponding number of cran'lispconnect- 4ing rods each of which connects'oneo said driving Holembers with one of the cranks, a

pump-connecting rod -pivoted to eachdriv'- ing member at thesame axis as'the crank connecting rod, a pump driven by each of said pump-connecting rods,.and a motor arranged' tobe operated. by thej'fliid' pro? i pelled'by said pumps. 1 l

10. A power transmissionicomprising an '.Linternal combustionengine having a --pluralityiof'driving members, a shaft having a correspondn numberof cranks,.`connecting rods each o wliicli'connects one of said driving members with` one of the cranks, a

`pump-connecting rod `pivoted to leach, driv ing meinberatthe same axis as the crank-4 connectin rod, a lever `connected. with ,the othervv en of the pump-connecting rod, a

Apump driven lby eachof said levers, and fa motor arranged` to be operated by the duid corresponding number of cranks, connectin '11. 'Ay power transmission comprising an internal icombustion engine having a plurality of drivingmembers, a shaft having 'a 'im 'rods eachjof which coi'inects ..one of sai driving 'memberswith oneof the craiilispa i connecting rod', 'a lever connected with the other end of the pump-connecting rod, an 'adjustable fulcrum for said lever, a pump 12. A power trans'missioii'compri'sing an internal combustion engine having a pluingV members `with oneof theorallks, iii-pumpconne'cting rod pivotedtoea'ch driving memvpump#connecting rod pivotedto each.'d'rifv#l Aing member at the same'axis as ,the cranlrl95 driven byeach of said levers, and a motor arranged to be operated bythe fluid proralityofgdrivingmembers, a yshaft having av corresponding number of lcranks,"conneoting *rodseachfof which connectsone-of said driv-V .los

ber-"atvl the samef-axis'fas the crank-connect-r i for ,'eachfQof said levers, 'a' arallel I connection v,betweensaid sides l ing'rod, a leverconnected with the:other'end`v` i 'of the puinpco'nnecting rod, ,a fulcrumsl'ide vliti 1011 -iompifisne ai plurality of operatively connected;butdifu ferentlyf timed driving members, levers act'ufated' by j's'aid. drivin 1 members, a` fu'lcrum slide/for eacl'i gf sai levers,`apparallel mo-y tion' connection between 4said slides, a 'pump driven by' `each'iof said levers, 'ai motor @framed tout@ 'Operated lby ne anni `pas pel-led by Said-pumps', Y I v plurality of operatively-connected but ferently timed driving members, llevers actuated by said driving members, apuinp 'operj iin @limi .I

said lever, and to l fsaid point, j

c to alineA with plurality ferently tuatedby said members,

each fulcrum into line with the atively connected with each of the said levers, a fulcrum for each lever, adjustable the point at .which the respective pump is connected with said lever, 2'and to difl'erentdistances from pelled by said pumps, and-a device for reversing the motor, said device being so arranged relatively to the fulcrum-adjusting means that the. latter will allow the reversmeans for adjusting said slides in'unison, a motor arranged to be propelled by the fluid propelled by said pumps, a device for reversing the'mot'or, and a projection connected wthsaid slides and normally extending into the path of the reversing debut arranged vice-toprevent its operation, 4 j

path when the fulcrums are in to clear said 'line' with the pump connections.

` ton arran f the pump, a motor adapted to be operated by a fluid under pressure,

through which the operating fluid will pass to the motor and returnlecting motor to the inlet `and prising a 16. A 4power transmission comprising apump, a motor 4adapted-to be operatedby 'fluid under pressure, connections from said 'to-the outlet of the a receptacleadapted to 'contain a of fluid, a replenishing pu-mp comcylinder permanently open to the lower portion of said receptacle, and a pispump, Supply take flui from said receptacle and to delivei s,uch fluid to that connection through l 4wliitzligthe :operating fluidv returns from the motor to the first-named pump. 17. A; power transmission comprising a pump, `a pocket -for collecting leakage from from the pump from the motor to the pump, means for coling `such leakage to said pocket, a receptacle arranged to lreceive the overflow from said pocket, and a-replenishing pump arranged to take fluid from said. receptacle and to said point, means for adjusting the fulcrums in unison, a mo-v tor arranged to be driven by the fluid pro-l difl'erent distances froml ed to work in said cylinder and to connections leakage from the motor and conveydeliver such fluid under pressure to that connection through which the operating fluid returns from the motor to the first-named pump.

18. vA power transmission comprising a pump, a motor adapted to be operated by fluid under pressure, connections from said motor to the inlet and to the outlet of the pump, a receptacle adapted to contain a supply of ing acylinder both ends of which have connections to said receptacle, one ofd said connections being permanently open, a suction valve controlling the other connection, and al piston arranged to work in said cylinder and to take fluid from said receptacle and to deliver such fluid to that connection through which the operating fluid returns `:from the motor to the first-named pump.

19. A power transmission comprising a pump, a motor adapted to be operated by fluid under pressure, y motor to the inlet and to the outlet of the pump, a receptacle adapted to contain a supply of fluid, an upright cylinder whose tion connection from the lower endl of said receptacle to the lower portion of said cylinder, and a replenishing piston arranged to 20. A .power transmission comprising a pump, a motor adapted to be operated by fluid under pressure,

connections from said motor vto the inlet and 'to the outlet of the pump', a receptacle adapted to contain a supply of fluid, a replenishing pump located at, and communicating with, the lower portion of the receptacle so as to be below the level of the fluidv in said receptacle, a suction connection from said receptacle to the replenishing pump, and a `delivery connection from the replenishing pump tothat connection through which the operating fluid returns from the motor to the firstnamed pump.

In testimony whereof I have signed this specification in the presence of two subscribing witnesses.

HARVEY D, WILLIAMS.

vWitnesses: JOHN Lo'rmA,

CHARLES fluid, a replenishing pump l,compris-- connections from said l upper end is open to said receptacle, a suc- 

